CN204420130U - Two-way thermal expansion valve - Google Patents
Two-way thermal expansion valve Download PDFInfo
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- CN204420130U CN204420130U CN201520015182.XU CN201520015182U CN204420130U CN 204420130 U CN204420130 U CN 204420130U CN 201520015182 U CN201520015182 U CN 201520015182U CN 204420130 U CN204420130 U CN 204420130U
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- spool
- heating power
- valve
- power expansion
- expansion valve
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Abstract
The utility model relates to a two-way thermal expansion valve, it includes: drive assembly, main valve body subassembly and adjusting part. The main valve body assembly includes a valve housing and a valve spool received in the valve housing. A valve housing includes a first end secured to the drive assembly and an opposite second end secured to the adjustment assembly, the valve housing including a first chamber and a second chamber separated by a valve seat portion. The valve spool includes a first end operatively connected to the drive assembly and an opposite second end operatively connected to the adjustment assembly, the second end being located within the second chamber, the valve spool including an abutment that mates with the valve seat portion. Wherein further included in the valve housing is a back pressure chamber between the drive assembly and the first end of the valve spool, the main valve body assembly including a passage configured for fluidly communicating the back pressure chamber and the second chamber with one another.
Description
Technical field
The utility model relates to a kind of two-way heating power expansion valve.
Background technique
Heating power expansion valve is the key element of the control system degree of superheat in refrigeration system, is generally installed between stock solution tube and vaporizer, and it realizes the pressure drop from condensing pressure to evaporating pressure, directly determines the ride quality of whole system.
Heating power expansion valve is by temperature-sensitive bag sensing evaporator terminal temperature, thus regulate its restriction aperture size, and then control flow to the mass flow rate of the refrigeration agent of vaporizer number and regulate vaporizer terminal temperature, to ensure that gaseous refrigerant flows to compressor, realize the compressor trouble free service under rational evaporation efficiency.
In the heating power expansion valve of prior art, when refrigeration agent forward flow (corresponding to cooling condition), the spool lower end of heating power expansion valve is arranged in the low-pressure cavity after throttling.And when refrigeration agent reverse flow (corresponding to heating condition), the spool lower end of heating power expansion valve is arranged in the hyperbaric chamber before throttling, what now refrigeration agent applied to spool upwards pressure than large during forward flow, the aperture of restriction is caused to be tending towards reducing, under making equal operating mode, refrigerant mass flow reduces, and system overheat degree becomes large.
Because single heating power expansion valve in refrigeration and can not provide identical system overheat degree under heating situation, therefore need to arrange two heating power expansion valves, it is respectively used to refrigeration and heats two kinds of situations, but which increases cost, and improves the possibility broken down.
In addition, existing heating power expansion valve part is more, complex structure, therefore manufacture and assembly cost higher, reliability is lower.
Therefore, there is the demand of the above defect for the heating power expansion valve solving prior art.
Model utility content
The purpose of this utility model is to provide a kind of two-way heating power expansion valve, and it can carry out the control of system overheat degree by means of only a heating power expansion valve, and when identical temperature-sensitive bag temperature, the degree of superheat of heating condition and cooling condition is suitable.
Another object of the present utility model is to provide a kind of two-way heating power expansion valve, and its number of spare parts is less, and structure is simple, can reduce manufacture and assembly cost, and improve reliability.
According to one side of the present utility model, provide a kind of two-way heating power expansion valve, it comprises: driven unit, main valve body assembly and adjusting part, main valve body assembly comprises: valve casing, valve casing comprises the first end being fixed to driven unit and the second contrary end being fixed to adjusting part, and valve casing comprises separated first chamber and the second chamber by seat portion; And the spool be contained in valve casing, spool comprises the first end being operatively connected to driven unit and the second contrary end being operatively connected to adjusting part, and the second end is positioned at the second chamber, and spool comprises the abutting part coordinated with seat portion; Wherein, also comprise the back pressure cavity between driven unit and the first end of spool in valve casing, main valve body assembly comprises the passage being configured for making back pressure cavity and the second chamber fluid communication with each other.
Alternatively, spool is the single type spool comprising spool main body and guide portion.
Alternatively, valve casing is provided with the support platform radially-inwardly protruded near first end, and guide portion extends through the central opening of support platform thus guided by central opening.
Alternatively, support platform supporting sealing member, to seal between guide portion and valve casing.
Alternatively, the second end of spool is provided with the step surface of annular, and step surface abuts with the spring of adjusting part.
Alternatively, between spool and valve casing, circumferential seal is provided with to provide sealing between back pressure cavity and the first chamber.
Alternatively, spool is formed with the circumferential recess of the part in formation first chamber, the wall portion of circumferential recess forms abutting part.
Alternatively, channel setting is in spool.
Alternatively, spool comprises spool main body and guide portion, and passage comprises the longitudinal section being arranged in spool main body and the radial section being arranged in guide portion.
Alternatively, longitudinal section comprises first paragraph and second segment, and the diameter of first paragraph is greater than the diameter of second segment.
Alternatively, it is characterized in that, be provided with in the channel and allow one-way valve from the second chamber to back pressure cavity that flow from of working medium, when the pressure in the second chamber be greater than make a reservation for open pressure time, one-way valve opens.
Alternatively, the predetermined pressure opened pressure and be less than the working medium entering two-way heating power expansion valve, and be greater than the pressure of the working medium of discharging from two-way heating power expansion valve.
Alternatively, passage is formed in the wall of valve casing.
Advantage according to the two-way heating power expansion valve of one or more embodiments of the present utility model is:
(1) space of the close driven unit side of spool is incorporated into by the pressure of the close adjusting part side by spool, making a concerted effort on spool is acted on by refrigeration agent when weakening refrigeration agent reverse flow, make in refrigeration and to heat the stressing conditions change of two kinds of operating mode lower valve cores little, the difference of system overheat degree is little.
(2) by adopting single type spool, making the reliability of heating power expansion valve higher, and easily processing passage therein.
(3) by coordinating between guide portion and the central opening of support platform, the guiding of spool can stably be realized.
(4) only heating the one-way valve opened in situation by arranging in the channel, refrigeration and the system overheat degree difference under heating two kinds of operating modes can reduced further.
(5) by arranging passage in the wall of valve casing, can avoid processing spool, ensureing that spool stably moves between two parties.
Accompanying drawing explanation
By the description referring to accompanying drawing, the feature and advantage of one or several embodiment of the present utility model will become easier to understand, wherein:
Fig. 1 is the schematic diagram of the cooling condition of the refrigeration system adopting two-way heating power expansion valve.
Fig. 2 is the schematic diagram of the heating condition of the refrigeration system adopting two-way heating power expansion valve.
Fig. 3 is the stereogram of the two-way heating power expansion valve according to the first mode of execution of the present utility model.
Fig. 4 is the exploded view of the two-way heating power expansion valve according to the first mode of execution of the present utility model.
Fig. 5 is the sectional view of the two-way heating power expansion valve according to the first mode of execution of the present utility model.
Fig. 6 is the sectional view of the spool of two-way heating power expansion valve according to the first mode of execution of the present utility model.
Fig. 7 shows the stressing conditions of the spool of the two-way heating power expansion valve according to the first mode of execution of the present utility model.
Fig. 8 is according to the sectional view of the two-way heating power expansion valve of the second mode of execution of the present utility model.
Fig. 9 is the sectional view of the two-way heating power expansion valve according to the 3rd mode of execution of the present utility model.
Embodiment
Description related to the preferred embodiment is only exemplary below, instead of the restriction to the utility model and application or usage.
In the following description mentioned " on ", D score, " top ", the direction such as " end " be only for the orientation of heating power expansion valve shown in accompanying drawing, and can change with the actual direction of heating power expansion valve.
The refrigeration system and working principle thereof that adopt according to two-way heating power expansion valve of the present utility model are described below with reference to Fig. 1 and Fig. 2.
Under cooling condition, as shown in Figure 1, the liquid refrigerant (working medium) of High Temperature High Pressure discharged by compressor 100, and refrigeration agent, entering the first heat exchanger coiled pipe 104 (as condenser) after four-way change-over valve 102, becomes the refrigeration agent of cryogenic high pressure.Subsequently after filter 106, refrigeration agent is from heating power expansion valve 200 (or 300,400, first interface 232 (entrance) down together) flows to heating power expansion valve (also referred to as forward flow), after its restriction generation orifice restriction, be expanded into the vaporific liquid refrigerant of low-temp low-pressure and discharge from the second interface 234 (outlet).Then refrigeration agent flows to the second heat exchanger coiled pipe 108 (as vaporizer), absorbs the gaseous refrigerant that heat becomes high-temperature low-pressure.After this refrigeration agent is through liquid storage barrel 110 to be separated the liquid that may exist, and gaseous refrigerant returns compressor 100, completes a refrigeration cycle.
Under heating condition, as shown in Figure 2, the liquid refrigerant of High Temperature High Pressure discharged by compressor 100, and refrigeration agent, entering the second heat exchanger coiled pipe 108 (as condenser) after four-way change-over valve 102, becomes the refrigeration agent of cryogenic high pressure.Then refrigeration agent flows to heating power expansion valve 200 (also referred to as reverse flow) from the second interface 234 (entrance) of heating power expansion valve 200, after its restriction generation orifice restriction, be expanded into the vaporific liquid refrigerant of low-temp low-pressure and discharge from first interface 232 (outlet).After filter 106, refrigeration agent flows to the first heat exchanger coiled pipe 104 (as vaporizer), absorbs the gaseous refrigerant that heat becomes high-temperature low-pressure.After this refrigeration agent is through liquid storage barrel 110 to be separated the liquid that may exist, and gaseous refrigerant returns compressor 100, completes one and heats circulation.
Temperature-sensitive bag 202 is arranged in the upstream of liquid storage barrel 110, provides corresponding pressure with the terminal temperature of sensing evaporator (first heat exchanger coiled pipe 104 or the second heat exchanger coiled pipe 108) via capillary tube 203 to heating power expansion valve.In addition, the refrigeration agent in refrigeration system is directed to the balance port (not shown) of two-way heating power expansion valve by balance tube 204.The pressure difference provided by temperature-sensitive bag 202 and balance tube 204 controls the restriction aperture of heating power expansion valve, and then controls the refrigerant flow entering vaporizer.
Referring to Fig. 3-7, the two-way heating power expansion valve 200 according to the utility model first mode of execution is described.As shown in Figure 3, Figure 4, two-way heating power expansion valve 200 comprises driven unit 210, main valve body assembly 230 and adjusting part 270 generally.
As shown in Figure 5, driven unit 210 comprises housing 212, and housing 212 is connected to the first end 242 of the valve casing 240 of main valve body assembly 230 hermetically.In housing 212, be embedded with diaphragm 214, the inner space of housing 212 is divided into upper chambers 216 and lower chamber 218 by diaphragm 214.Be provided with cushion plate 215 below diaphragm 214, it is against the first end 252 of the spool 250 in main valve body assembly 230, so that the power suffered by diaphragm 214 is passed to spool 250.
The spool 250 that main valve body assembly 230 comprises valve casing 240 and is contained in valve casing 240.For clarity, spool 250 amplifies in figure 6 and illustrates.As described above, the first end 242 (being upper end in figure) of valve casing 240 is fixed to driven unit 210.Second end 246 (being lower end in figure) of valve casing 240 is fixed to adjusting part 270 (will describe in detail below).Valve casing 240 comprises for the inflow of refrigeration agent and the first interface 232 of outflow and the second interface 234 (for the purpose of illustrative clarity, a part for first interface 232 and the second interface 234 being only shown).Correspondingly, the first end 252 of spool 250 is operatively connected to driven unit 210, and the second end 256 of spool 250 is operatively connected to adjusting part 270, and be arranged in the second chamber 259 (will describe in detail below), thus, driven unit 210 and adjusting part 270 apply the contrary power in direction to spool 250, to maintain the suitable aperture of restriction.
Spool 250 can be the single type spool 250 comprising guide portion 251 and spool main body 254.Radial outstanding support platform 243 is provided with near valve casing first end 242.The diameter of guide portion 251 is less than the diameter of spool main body 254, thus forms end face 253 at the top of spool main body 254.Guide portion 251 extends through the central opening of support platform 243, thus spool 250 can be shifted up and down under the guiding of this central opening.Between the end face 253 and the bottom surface 247 of support platform 243 of spool main body 254, (in other words, between driven unit 210 and the first end 252 of spool 250) forms back pressure cavity 236.Lip packing 237 is had at support platform 243 upper support, lip packing 237 flexibly against the outer wall of guide portion 251 and the inwall of valve casing 240, with the lower chamber 218 preventing the refrigeration agent in the first chamber 258 or back pressure cavity 236 (described below) from entering into driven unit 210.
The internal diameter of the diameter of spool main body 254 and a part for valve casing 240 matches, and spool main body 254 can be shifted up and down in valve casing 240.In the inwall of valve casing 240, the diameter due to the position corresponding from first interface 232 and the position corresponding with the second interface 234 is different and form step, forms seat portion 245 at step place.The inner space of valve casing 240 is divided into the first chamber 258 be communicated with first interface 232 and the second chamber 259 be communicated with the second interface 234 by seat portion 245.In spool main body 254, the position corresponding with first interface be formed with a part of circumferential recess 257 (see Fig. 6) in formation first chamber 258, forms abutting part 255 by the wall of circumferential recess 257.The abutting part 255 of spool 250 matches with the seat portion 245 of valve casing 240, to form restriction 235 between.In the present embodiment, abutting part 255 is formed by the wall portion (inclined floor near adjusting part 210 side) of the circumferential recess 257 in spool main body 254.Should be appreciated that abutting part 255 is not limited to this form, but can be other form that can engage with seat portion 245 or be separated.
When refrigeration agent forward flow, the high-pressure refrigerant being arranged in the first chamber 258, after this restriction 235, expand into the low pressure refrigerant in the second chamber 259; And when refrigeration agent reverse flow, be arranged in the high-pressure refrigerant in the second chamber 259 after this restriction 235, expand into the low pressure refrigerant in the first chamber 258.
See Fig. 6, in spool 250, be formed with passage 260 to make the space fluid communication with each other of the longitudinal both sides of spool 250, that is, make back pressure cavity 236 be communicated with second chamber 259 at the second end 256 place of spool 250.This passage 260 comprises the longitudinal section 262 arranged coaxially and the radial section 263 being positioned at guide portion 251 that are positioned at spool main body 254.Alternatively, this longitudinal section 262 comprises the first paragraph 262a and superposed second segment 262b that are positioned at bottom, and the diameter of first paragraph 262a is greater than the diameter of second segment 262b.Should be appreciated that passage 260 also can only be arranged in spool main body 254, and in end face 253 upper shed.Such as, passage 260 can comprise longitudinal section and oblique section.
Preferably, between back pressure cavity 236 and the first chamber 258, spool 250 is formed peripheral groove 264, in groove, is provided with O-ring seals 266, thus realize the sealing between spool 250 and valve casing 240.Should be appreciated that peripheral groove also can be arranged on valve casing 240.
Adjusting part 270 is arranged on the below of main valve body assembly 230.Adjusting part 270 comprises: base 272, and base 272 is fixed to the second end 246 of valve casing 240 hermetically; Through the adjusting nut 274 that base 272 extends, adjusting nut 274 hermetically, is rotatably fixed to base 272, thus can regulate from base 272 external hand; The spring 276 supported by adjusting nut 274, the upper end of spring 276 abuts the annular table terrace of the second end 256 of spool 250; And lid 278, lid 278 screws to base 272, to protect adjusting nut 274 can not by false touch.
The working principle of the two-way heating power expansion valve 200 according to the utility model first mode of execution is described below.
The heating power expansion valve 200 schematically shown in Fig. 1-7 is outer balanced type expansion valves.See Fig. 1, in the downstream of vaporizer, the pipeline of the upstream end of liquid storage barrel 110 is outside equipped with temperature-sensitive bag 202.What fill in temperature-sensitive bag 202 is the refrigeration agent being in vapor liquid equilibrium saturation state, and this part refrigeration agent does not communicate with intrasystem refrigeration agent.Temperature-sensitive bag 202 and refrigerant line close contact are to experience the superheated vapor temperature of evaporator outlet, refrigeration agent due to its inside is saturated, so the saturation pressure transmitted at this temperature to be passed to the upper chambers 216 above the diaphragm 214 in heating power expansion valve 200, apply downward pressure Fc (see Fig. 7) to diaphragm 214.In addition, thinner balance tube 204 extends to the lower chamber 218 below diaphragm 214 from the refrigerant line corresponding with the position residing for temperature-sensitive bag 202, to apply evaporator pressure Fe upwards to diaphragm 214.
Pressure Fc and Fe is passed to spool 250 by cushion plate 215.In addition, spool 250 is also subject to the fluid force F that the spring force Fs upwards from the spring 276 of adjusting part 270 and the fluid pressure differential by spool about 250 both sides produce
4.Spool 250 is in state of equilibrium under the effect of these power, that is, Fc-Fe-Fs-F
4=0, thus the aperture making that restriction 235 keeps suitable.
Under heating condition (refrigeration agent reverse flow), high-pressure refrigerant flows into the second chamber 259 from the second interface 234, this high-pressure refrigerant can flow in back pressure cavity 236 via passage 260, that is, be incorporated into above spool 250 by the pressure below spool 250.Thus, the refrigerant pressure suffered by bottom surface of spool 250 is offset by the refrigerant pressure in back pressure cavity 236 at least in part.Compared with the situation of passage is not set in spool, weaken the fluid force F upwards acted on spool 250
4, to make in refrigeration and to heat the stressing conditions change of two kinds of operating mode lower valve cores 250 little, thus make the difference of system overheat degree little, to meet the bidirectional flow function under the same degree of superheat setting of the same heating power expansion valve of same system.
Ensure that by arranging O-ring seals 266 in spool main body 254 and realize above function.Specifically, seal ring 266 ensure that when reverse flow, the high-pressure refrigerant entered from the second interface 234 is after entering back pressure cavity 236 through passage 260, from back pressure cavity 236, the first chamber 258 can not be flow to via the gap between spool 250 and valve casing 240, cause the pressure leakage in back pressure cavity 236.If do not arrange independent Sealing, then because the pressure in back pressure cavity 236 is higher than the pressure at first interface 232 (import) place, pressure in back pressure cavity 236 is easy to via this gap (due to spool 250 and valve casing 240 relative shift between this, this gap certainly exists) and leak, thus do not have fully weakening fluid force F
4effect.In addition, sealing circle 266 also assures that under refrigeration or heating condition, the high-pressure refrigerant flowed into from first interface 232 or the second interface 234 can not be leaked to another interface via passage 260 and this gap, thus the fluid avoided without throttling enters into low-pressure cavity and enters vaporizer, this fluid leaks and can produce harmful effect to the degree of superheat of expansion valve.
In addition, be the single type spool comprising guide portion 251 and spool main body 254 according to the spool 250 of this mode of execution, compared with the spool formed with multiple part, the reliability of single type spool is higher, is easier to manufacture, and inner passage does not exist any leakage point.In addition, guided by support platform 243 by guide portion 251, stably can realize the guiding of spool, that is, the moving direction of spool is parallel with spool inwall all the time, with the inclination avoiding spool may occur in movement process.Further, because spool 250 is single types, so easily process passage therein.Particularly, longitudinal section 262 of passage 260 wherein can be arranged to comprise the larger first paragraph 262a of diameter being positioned at below and the less second segment 262b of the diameter being positioned at top, these designs especially conveniently carry out machining.
Although above-described spool 250 is the one-piece member comprising guide portion 251 and spool main body 254, guide portion 251 also can be the separate part independent of spool main body 254.In addition, although the second end 256 of above-described spool 250 is directly supported by spring 276, also can be provided with by spring-supported bearing, this bearing supports spool in the mode of precise alignment.
Below with reference to the two-way heating power expansion valve 300 of Fig. 6 introduction according to the second mode of execution of the present utility model, will no longer the parts identical with the first mode of execution be described in detail.
As shown in Figure 6, in the spool 350 of heating power expansion valve 300, be provided with passage 260 equally, passage 260 comprises the longitudinal section 262 and superposed radial section 264 that are positioned at bottom, and radial section 264 leads to back pressure cavity 236.To be provided with the point of intersection of radial section 264 in longitudinal section 262 and to allow condenser (working medium) from the second chamber 259 to the one-way valve 366 (schematically showing in the drawings) that back pressure cavity 236 flows.This one-way valve 366 is arranged to have and predetermined is opened pressure, make to only have when passage 260 inside pressure (pressure in the second chamber 259) higher than predetermined open pressure time open, with allow the pressure in the second chamber 259 and the pressure in back pressure cavity 236 through.And when the pressure in passage 260 be less than predetermined open pressure time, one-way valve 366 is closed.In addition, even if the pressure in back pressure cavity 236 opens pressure higher than predetermined, one-way valve 366 also keeps closing.
Predetermined pressure setting of opening becomes to be less than the high-pressure refrigerant pressure that enters heating power expansion valve 300 and is greater than the low pressure refrigerant pressure leaving heating power expansion valve 300.Under cooling condition, the pressure in the second chamber 259 be communicated with passage 260 is low pressure refrigerant pressure, and now one-way valve 366 is closed, and the working state of heating power expansion valve 300 is similar to the working state of the common heating power expansion valve not arranging passage 260.And under heating condition, refrigeration agent reverse flow, pressure in the second chamber 259 be communicated with passage 260 is high-pressure refrigerant pressure, now one-way valve 366 is opened, make the pressure in back pressure cavity 236 and the second chamber 259 through, during to weaken refrigeration agent reverse flow, act on the fluid force F upwards on spool 250
4, realize the effect identical with the heating power expansion valve 200 of above first mode of execution.
According to the heating power expansion valve 300 of this mode of execution, under cooling condition, allow the pressure of low pressure refrigerant to act on spool 260, and under heating condition, weaken high-pressure refrigerant at least in part act on fluid force on spool 260, thus, the hydrokinetic difference suffered by two kinds of operating mode lower valve cores can be reduced further, thus reduce the difference of the system overheat degree under two kinds of operating modes further.
Below with reference to the two-way heating power expansion valve 400 of Fig. 7 introduction according to the 3rd mode of execution of the present utility model, will no longer the parts identical with the first mode of execution be described in detail.
Two-way heating power expansion valve 400 is with the difference of above first mode of execution, passage 460 is not arranged in spool 450, but be arranged in the wall of valve casing 440, and back pressure cavity 236 is extended near the second interface 234, thus the second chamber 259 is communicated with back pressure cavity 236 fluid.Thereby, it is possible to realize the effect same with the first mode of execution, that is, act on the fluid force F upwards on spool 450 when weakening refrigeration agent reverse flow
4, little to ensure heating power expansion valve system overheat degree difference when forward and reverse flow.The processing of two-way heating power expansion valve 400 is very simple, further, due to without the need to arranging passage in spool, have an impact so avoid the balance of process to spool 450 processing passage in spool, that is, spool 450 can stably move between two parties in valve casing 440.
Although described various mode of execution of the present utility model in detail at this, but should be appreciated that the utility model is not limited to the embodiment described in detail and illustrate here, other modification and variant can be realized when not departing from essence of the present utility model and scope by those skilled in the art.All these modification and variant all fall in scope of the present utility model.And all components described here can be replaced by component equivalent in other technologies.
Claims (13)
1. a two-way heating power expansion valve (200,300,400), it is characterized in that comprising: driven unit (210), main valve body assembly (230) and adjusting part (270), described main valve body assembly (230) comprising:
Valve casing (240), described valve casing (240) comprises the first end (242) being fixed to driven unit (210) and contrary the second end (246) being fixed to adjusting part (270), and described valve casing (240) comprises separated first chamber (258) and the second chamber (259) by seat portion (245); And
Be contained in the spool (250) in described valve casing (240), described spool (250) comprises the first end (252) being operatively connected to described driven unit (210) and contrary the second end (256) being operatively connected to described adjusting part (270), described second end (256) is positioned at described second chamber (259), and described spool (250) comprises the abutting part (255) coordinated with described seat portion (245);
Wherein, the back pressure cavity (236) between the first end (252) being positioned at described driven unit (210) and described spool (250) is also comprised in described valve casing (240), described main valve body assembly (230) comprises the passage (260,460) being configured for making described back pressure cavity (236) and described second chamber (259) fluid communication with each other.
2. two-way heating power expansion valve according to claim 1 (200,300,400), is characterized in that, described spool (250) is the single type spool comprising spool main body (254) and guide portion (251).
3. two-way heating power expansion valve (200 according to claim 2,300,400), it is characterized in that, described valve casing (240) is provided with the support platform (243) radially-inwardly protruded near first end (242), and described guide portion (251) extends through the central opening of described support platform (243) thus guided by described central opening.
4. two-way heating power expansion valve (200 according to claim 3,300,400), it is characterized in that, described support platform (243) supporting sealing member (237), to seal between described guide portion (251) and described valve casing (240).
5. two-way heating power expansion valve (200 according to claim 1,300,400), it is characterized in that, second end (256) of described spool (250) is provided with the step surface of annular, and described step surface abuts with the spring (276) of described adjusting part (270).
6. two-way heating power expansion valve (200 according to claim 1,300,400), it is characterized in that, between described spool (250) and described valve casing (240), be provided with circumferential seal (266) to provide sealing between described back pressure cavity (236) and described first chamber (258).
7. two-way heating power expansion valve (200 according to claim 1,300,400), it is characterized in that, described spool (250) is formed the circumferential recess (257) of the part forming described first chamber (258), and the wall portion of described circumferential recess (257) forms described abutting part (255).
8. two-way heating power expansion valve according to claim 1 (200), is characterized in that, described passage (260) is arranged in described spool (250).
9. two-way heating power expansion valve according to claim 8 (200), it is characterized in that, described spool (250) comprises spool main body (254) and guide portion (251), and described passage (260) comprises the longitudinal section (262) being arranged in described spool main body (254) and the radial section (263) being arranged in described guide portion (251).
10. two-way heating power expansion valve according to claim 9 (200), it is characterized in that, described longitudinal section (262) comprises first paragraph (262a) and second segment (262a), and the diameter of described first paragraph (262a) is greater than the diameter of described second segment (262a).
11. two-way heating power expansion valves (300) according to any one in claim 1 to 10, it is characterized in that, the one-way valve (366) allowing working medium to flow from described second chamber (259) to described back pressure cavity (236) is provided with in described passage (260), when the pressure in described second chamber (259) be greater than predetermined open pressure time, described one-way valve (366) is opened.
12. two-way heating power expansion valves according to claim 11 (300), it is characterized in that, the described predetermined pressure opened pressure and be less than the working medium entering described two-way heating power expansion valve (300), and be greater than the pressure of the working medium of discharging from described two-way heating power expansion valve (300).
13. two-way heating power expansion valves (400) according to any one in claim 1 to 7, it is characterized in that, described passage (460) is formed in the wall of described valve casing (240).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520015182.XU CN204420130U (en) | 2015-01-09 | 2015-01-09 | Two-way thermal expansion valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520015182.XU CN204420130U (en) | 2015-01-09 | 2015-01-09 | Two-way thermal expansion valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204420130U true CN204420130U (en) | 2015-06-24 |
Family
ID=53470501
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520015182.XU Withdrawn - After Issue CN204420130U (en) | 2015-01-09 | 2015-01-09 | Two-way thermal expansion valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204420130U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105674637A (en) * | 2016-01-13 | 2016-06-15 | 同济大学 | Refrigerating fluid expansion valve based on differential pressure self-regulation |
| CN105822770A (en) * | 2015-01-09 | 2016-08-03 | 艾默生环境优化技术(苏州)有限公司 | Two-way thermal expansion valve |
-
2015
- 2015-01-09 CN CN201520015182.XU patent/CN204420130U/en not_active Withdrawn - After Issue
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105822770A (en) * | 2015-01-09 | 2016-08-03 | 艾默生环境优化技术(苏州)有限公司 | Two-way thermal expansion valve |
| CN105822770B (en) * | 2015-01-09 | 2019-10-29 | 艾默生环境优化技术(苏州)有限公司 | Two-way thermal expansion valve |
| CN105674637A (en) * | 2016-01-13 | 2016-06-15 | 同济大学 | Refrigerating fluid expansion valve based on differential pressure self-regulation |
| CN105674637B (en) * | 2016-01-13 | 2017-12-15 | 同济大学 | A kind of refrigerant expansion valve based on pressure difference self-regulation |
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